CA3037586C - Load-measuring hydraulic cylinder - Google Patents
Load-measuring hydraulic cylinder Download PDFInfo
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- CA3037586C CA3037586C CA3037586A CA3037586A CA3037586C CA 3037586 C CA3037586 C CA 3037586C CA 3037586 A CA3037586 A CA 3037586A CA 3037586 A CA3037586 A CA 3037586A CA 3037586 C CA3037586 C CA 3037586C
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- 239000012530 fluid Substances 0.000 claims abstract description 129
- 238000000034 method Methods 0.000 claims abstract description 21
- 238000012544 monitoring process Methods 0.000 claims abstract description 14
- 238000010438 heat treatment Methods 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L19/00—Details of, or accessories for, apparatus for measuring steady or quasi-steady pressure of a fluent medium insofar as such details or accessories are not special to particular types of pressure gauges
- G01L19/04—Means for compensating for effects of changes of temperature, i.e. other than electric compensation
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
- E21B19/22—Handling reeled pipe or rod units, e.g. flexible drilling pipes
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
- G01L5/0061—Force sensors associated with industrial machines or actuators
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
- G01L5/0061—Force sensors associated with industrial machines or actuators
- G01L5/0071—Specific indicating arrangements, e.g. of overload
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- Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Mining & Mineral Resources (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Fluid Mechanics (AREA)
- Environmental & Geological Engineering (AREA)
- Mechanical Engineering (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Fluid-Pressure Circuits (AREA)
- Actuator (AREA)
- Force Measurement Appropriate To Specific Purposes (AREA)
- Information Retrieval, Db Structures And Fs Structures Therefor (AREA)
Abstract
L'invention concerne une structure articulée comprenant une articulation qui peut être actionnée au moyen d'un vérin hydraulique. Un procédé de surveillance d'une charge appliquée à la structure articulée consiste à laisser s'échapper du fluide hydraulique du vérin hydraulique d'une manière qui compense l'expansion du fluide hydraulique provoquée par des variations de température du fluide hydraulique. Le procédé consiste en outre à mesurer la pression du fluide hydraulique dans le vérin hydraulique. Le vérin hydraulique peut faire partie d'un injecteur de tube de production concentrique. La charge appliquée au vérin hydraulique peut être utilisée pour indiquer une surcharge du guide de tube de production.The invention relates to an articulated structure comprising a joint which can be actuated by means of a hydraulic cylinder. A method of monitoring a load applied to the articulated structure includes leaking hydraulic fluid from the hydraulic cylinder in a manner that compensates for expansion of the hydraulic fluid caused by variations in temperature of the hydraulic fluid. The method further includes measuring the pressure of the hydraulic fluid in the hydraulic cylinder. The hydraulic cylinder may be part of a concentric production tube injector. The load applied to the hydraulic cylinder can be used to indicate production tube guide overload.
Description
BACKGROUND
[0001] This disclosure relates to methods and apparatus for measuring the load applied to a hydraulic cylinder by using a pressure sensor. The hydraulic cylinder may be part of a coiled tubing injector having a tubing guide. The load applied to the hydraulic cylinder may be used to indicate overload of the tubing guide.
BRIEF SUMMARY OF THE DISCLOSURE
The first check valve may prevent the flow of hydraulic fluid out of the variable chamber when in the closed position. In some embodiments, the constant-pressure supply of hydraulic fluid may comprise a source of pressurized hydraulic fluid and an accumulator. The accumulator may be intermittently coupled to the source of pressurized hydraulic fluid through a second check valve. The first and second check valves may be coupled by a second flowline. The accumulator may be coupled to the second flowline. The constant-pressure supply of hydraulic fluid may further comprise a reducing valve for regulating the pressure of the supplied hydraulic fluid.
The pressure sensor may be coupled to the variable chamber by a pressure path.
The pressure path may couple the pressure sensor to one of the variable chamber or the first flowline.
flowpath fluidly coupled to the variable chamber may be selectively opened based on a comparison between the measured position and the first position. A valve obturating the flowpath may be actuated to leak the hydraulic fluid from the variable chamber.
BRi ______________________ I-F DESCRIPTION OF THE DRAWINGS
DETAILED DESCRIPTION
[00311 It is to be understood that the following disclosure describes several exemplary embodiments for implementing different features, structures, or functions of the invention.
Exemplary embodiments of components, arrangements, and configurations are described below to simplify the disclosure; however, these exemplary embodiments are provided merely as examples and are not intended to limit the scope of the invention. Additionally, the disclosure may repeat reference numerals and/or letters in the various exemplary embodiments and across the Figures provided herein. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various exemplary embodiments and/or configurations discussed in the various figures. Moreover, the formation of a first feature over or on a second feature in the description that follows may include embodiments in which the first and second features are formed in direct contact, and may also include embodiments in which additional features may be formed interposing the first and second features, such that the first and second features may not be in direct contact. Finally, the exemplary embodiments presented below may be combined in any combination of ways, i.e., any element from one exemplary embodiment may be used in any other exemplary embodiment, without departing from the scope of the disclosure.
[0032] Additionally, certain terms are used throughout the following description and claims to refer to particular components. As one skilled in the art will appreciate, various entities may refer to the same component by different names, and as such, the naming convention for the elements described herein is not intended to limit the scope of the invention, unless otherwise specifically defined herein. Further, the naming convention used herein is not intended to distinguish between components that differ in name but not function. Additionally, in the following discussion and in the claims, the terms "including" and "comprising" are used in an open-ended fashion, and thus should be interpreted to mean "including, but not limited to." All numerical values in this disclosure may not be exact unless otherwise specifically stated. Accordingly, various embodiments of the disclosure may deviate from the numbers, values, and ranges disclosed herein without departing from the intended scope. Furthermore, as it is used in the claims or specification, the term "or" is intended to encompass both exclusive and inclusive cases, i.e., "A or B" is intended to be synonymous with "at least one of A and B," unless otherwise expressly specified herein.
[0033] Figure 1 shows an example load-measuring actuator including a hydraulic cylinder 12. The load-measuring actuator is connected to a source 100 of pressurized hydraulic fluid and to a drain 102, for example with quick-connects 40a and 40b. The hydraulic cylinder 12 has a variable chamber 10. The variable chamber 10 is delimited by a piston 18 reciprocally disposed in the hydraulic cylinder 12. The variable chamber 10 may be located on the cap side of the hydraulic cylinder 12.
[0034] The load-measuring actuator shown in Figure 1 comprises a constant-pressure supply 104 of hydraulic fluid. The constant-pressure supply 104 is connected to the variable chamber 10 through a first check valve 14. The first check valve 14 may be a normally-closed, pilot-to-open check valve. The first check valve 14 may be coupled to the variable chamber 10 via a first flowline 22. The first check valve 14 may prevent the flow of hydraulic fluid out of the variable chamber 10 when in the closed position.
[0035] In the load-measuring actuator shown in Figure 1, the constant-pressure supply 104 of hydraulic fluid may comprise the source 100 of pressurized hydraulic fluid and an accumulator 60.
The accumulator 60 may be intermittently coupled to the source 100 of pressurized hydraulic fluid through a second check valve 50. The first and second check valves, respectively 14 and 50, may be coupled by a second flowline 52. The accumulator may be coupled to the second flowline 52.
The constant-pressure supply 104 may further comprise a reducing valve 30 for regulating the pressure of the hydraulic fluid. A manual valve 70 may be provided to vent the accumulator 60 when the load-measuring actuator is not in operation.
[0036] The first check valve 14 may provide several advantages. First, it may protect the accumulator 60 from excessive pressure levels that may be generated by the load applied to the hydraulic cylinder 12. Second, even if the load applied to the hydraulic cylinder 12 does not generate an excessive pressure level, the check valve 14 may prevent fluid flow out of the variable chamber 10 into the accumulator 60 and may help maintain the hydraulic cylinder 12 in its extended position.
[0037] In the example of Figure 1, the source 100 may not be configured to supply constant pressure to the cap side of the cylinder 12. Instead, the constant-pressure supply may be provided to the cylinder 12 by the accumulator 60 pre-charged with gas at a pressure slightly below that of the source 100. In operation, hydraulic fluid may be intermittently supplied from the source 100 to the accumulator 60 by switching the position of a direction control valve 20.
Otherwise, the direction control valve 20 may remain in the neutral position. The check valve 50 may be used to maintain the hydraulic fluid in the accumulator 60 while the source 100 is not engaged. The check valve 50 may thus prevent flow back from the accumulator 60 toward the source 100. The hydraulic fluid in the accumulator 60 may remain at an essentially constant pressure, which is the pre-charging pressure. By connecting the accumulator 60 to the chamber of the hydraulic cylinder 12 via the first and second flowlines, respectively 22 and 52, hydraulic fluid may be supplied to the hydraulic cylinder 12 at the constant pressure level.
[0038] The load-measuring actuator shown in Figure 1 further comprises a pressure sensor 90.
The pressure sensor 90 is coupled to the variable chamber by a pressure path 92. The pressure path 92 may couple the pressure sensor 90 to the first flowline 22. Alternatively, the pressure path 92 may couple the pressure sensor 90 to the variable chamber 10.
[0039] The load-measuring actuator shown in Figure 1 further comprises a restricted flow orifice 80. The restricted flow orifice 80 may continuously leak hydraulic fluid from the variable chamber 10. The restricted flow orifice 80 may be coupled to the pressure path 92.
Alternatively, the restricted flow orifice 80 may be coupled to variable chamber 10 or the first flowline 22. The restricted flow orifice 80 may comprise a variable orifice valve, such as a needle valve.
[0040] The restricted flow orifice 80 may meter sufficiently low leakage rates. Preferably, the restricted flow orifice 80 may permit adjustment of its leakage rate, for example, to account for a dependence of the leakage rate on the ambient temperature, the viscosity of the hydraulic fluid, and/or the operating pressure of the load-measuring actuator. A needle valve may be a preferred embodiment of the restricted flow orifice 80 that meets these characteristics;
however, other embodiments may be sufficient, or even optimal, depending on the application of the load-measuring actuator. A fixed orifice valve is an example of an embodiment of a restricted flow orifice 80.
[0041] The restricted flow orifice 80 may allow a very low leakage rate from the cap side of the cylinder 12 back to the drain 102. The very low leakage rate may be compensated by supplying hydraulic fluid with the constant-pressure supply 104. Thus, in the absence of fluctuation of the load applied to the cylinder 12, the pressure measured by the sensor 90 remains at the constant pressure level.
[0042] The restricted flow orifice 80 may be sized so that the hydraulic fluid is leaked at a rate sufficient to compensate for the expansion of the hydraulic fluid caused by variations in temperature of the hydraulic fluid. Thus, volume increases caused by variations in temperature are discharged through the restricted flow orifice 80 without increasing the pressure in the hydraulic fluid. Moreover, in the absence of fluctuation of the load applied to the cylinder 12, the pressure measured by the sensor 90 remains at the constant pressure level even when environmental temperature increases or heating (e.g., from sunshine) causes thermal expansion of the hydraulic fluid in the cylinder 12.
[0043] In contrast with temperature increases, when the load applied to the hydraulic cylinder increases beyond a pre-selected threshold, the hydraulic fluid is leaked at a rate that is preferably insufficient to compensate for the increase of the load applied to the hydraulic cylinder. The pre-selected threshold for the load may correspond to the load that overcomes the constant pressure level supplied to the hydraulic cylinder 12. Thus, when the pressure measured by the sensor 90 exceeds the constant pressure level of the hydraulic fluid supplied to the variable chamber 10, the measured pressure is indicative of an increase of the load applied to the cylinder 12 beyond the pre-selected threshold. Moreover, the measured pressure is not indicative of the thermal expansion of the hydraulic fluid in the cylinder 12.
[0044] The leakage rate sufficient to compensate for the expansion of the hydraulic fluid caused by variations in temperature is at least equal to the expansion rate of a particular volume of hydraulic fluid corresponding to the maximum temperature increase rate observable during the day. The particular volume may be the volume of hydraulic fluid trapped in the variable chamber 10 when the hydraulic cylinder 12 is extended. However, the leakage rate may typically be larger than the expansion rate of the particular volume. Reasons for increasing the safety factor may include taking into account expansion in the volume of fluid in the first flowline 22 and the pressure path 92 and taking into account temperature increase rates larger than expected.
Reasons for decreasing the safety factor may include excessive drifting of the load-sensing actuator from its extended position caused by insufficient supply of hydraulic fluid at the constant pressure. When a needle valve is used, the leakage rate may be adjusted by trial and error as the needle valve position may depend on various parameters such as the constant pressure level at which hydraulic fluid is supplied, the viscosity of the hydraulic fluid, or the actual temperature increase rate.
[0045] As shown in Figure 1, the load-sensing actuator is configured to sense the load applied to a cylinder when the cylinder is extended. Given the benefit of this disclosure, those having ordinary skills will appreciate that a load-sensing actuator (not shown) may be configured to sense the load applied to the cylinder when the cylinder is retracted. In such cases, the constant-pressure supply, the pressure sensor, and the restricted flow orifice would be connected to the variable chamber located on the rod side of the hydraulic cylinder.
[0046] As shown in Figure 1, the restricted flow orifice 80 is implemented using only one valve.
However, the restricted flow orifice 80 may alternatively be implemented using a plurality of valves placed in series or in parallel.
[0047] Turning now to Figure 2, an example of a simplified load-measuring actuator is illustrated.
While the source 100 shown in Figure 1 may not be configured to supply constant pressure, a constant-pressure supply 104 is made available at the quick-connect 40a in Figure 2. As such, the accumulator 60 and the second check valve 50 may not be implemented. In addition, the direction control valve 20 may remain in the extend position, that is, in the position coupling the constant-pressure supply 104 to the cap side of the hydraulic cylinder 12 and the drain 102 to the rod side of the hydraulic cylinder 12.
[0048] The load-measuring actuator shown in Figure 1 or 2 may be used to counter the effects of thermal expansion in the hydraulic fluid and more accurately detelinine the load on hinged structures wherein the structure hinges are actuatable using a hydraulic cylinder. For example, as illustrated in Figures 3 and 3A, the load-measuring actuator shown in Figure 1 or 2 may be used in a coiled tubing injector 200 to more accurately determine the load on a tubing guide 106 of the coiled tubing injector 200.
[0049] As shown in Figures 3 and 3A, the coiled tubing injector 200 comprises an injector head 220 mounted within a cage or frame 210. The frame 210 protects the injector head 220 and allows it to be lifted by a crane or supported on a structure above a wellhead to accommodate a riser extending from the wellhead. A proximal end of the arched tubing guide 106 is coupled to the top of frame 210. Its distal end is free and oriented toward a reel (not shown) on which coiled tubing 108 is wound. The arched tubing guide 106 transitions the coiled tubing 108 between the reel and the top of the injector head 220. A plurality of rollers (not visible, except for the ends of pins 109 on which the rollers are mounted) are spaced along the length of the arched tubing guide 106. The tension on the coiled tubing 108 exerts loads on the arched tubing guide 106.
[0050] In the embodiment illustrated in Figures 3 and 3A, the arched tubing guide 106 is comprised of two segments, respectively 106a and 106b, so that the coiled tubing injector 200 can be more easily transported. Segment 106a is connected to the top of frame 210.
This connection could be rigid or made through a joint that allows for pivoting. Segment 106b is connected to segment 106a by a hinged joint 106c that allows segment 106b to pivot downwardly and inwardly toward the frame 210, for transport. When the coiled tubing injector is rigged, segment 106b is pivoted to operating position.
[0051] Also in the illustrated embodiment, a strut 110 supports the arched tubing guide 106 and transfers to frame 210 at least some of the loads generated by tension on the coiled tubing 108. A
distal end 110b of the strut 110 is coupled near the distal end of the arched tubing guide 106, preferably along segment 106b. A proximal end 110a of the strut 110 is coupled to frame 210.
The coupling at each end of the joint is, in this example, through pivoting joints. The load on the strut 110 is primarily a compressive force.
[0052] Referring to Figure 3A, the strut 110 may comprise of an "A" shaped frame 112 to aid the transfer of side bending moments to frame 210. Strut 110 further comprises a hydraulic cylinder 114. Connected to a distal end of the hydraulic cylinder 114 is a tang 122 that forms the distal end 110b of the strut 110 and couples to tubing guide 106. In this example, the strut 110 is designed to be collapsible to accommodate the folding of the arched tubing guide 106 by the pivoting of segment 106b. When segment 106b is pivoted up into an operational position, the hydraulic cylinder 114 is pressurized to carry a compressive load. Side forces and bending moments placed on the distal end of the hydraulic cylinder 114 are transferred to the "A"
frame 112 by support 116.
The pivoting joints at each end 110a and 110b of the strut 110 accommodate its movement. The bottom end of the hydraulic cylinder 114 may be connected to cross member 121 of the "A" frame 112 by a clevis and pin capable of carrying side loads.
[0053] The strut 110 makes use of a pressure sensor 302 connected to a port on hydraulic cylinder 114. The pressure sensor 302 generates a signal that is transmitted back to remotely located electronics components. The signal is indicative of the axial or compressive load on the strut 110, which in turn is caused by the load exerted on the tubing guide 106 by the tension of the coiled tubing 108. The electronic components may be configured to interpret and remotely display the signal from the pressure sensor 302. For example, the electronic components may be configured to detect whether the measured pressure exceeds the constant pressure level of the hydraulic fluid supplied to the hydraulic cylinder 114 and to convert the excess pressure into a compressive load corresponding to the measured pressure.
[0054] Additional consideration may be given to three design features: the reference pressure level in the cylinder 114 that would overcome the maximum load to which the tubing guide 106 is rated, the selection of the constant pressure supplied to the hydraulic cylinder 114, and the maximum pressure ratings of the cylinder 114 and pressure sensor 302.
[0055] For example, the cylinder 114 may be sized so that at the tubing guide's rated load, the pressure in the cylinder (referred to as the reference pressure level) is 3,000 psi.
[0056] The pressure level provided by the constant-pressure supply 104 (in Figure 1 or 2) to extend the cylinder 114 and may be selected at 1,500 psi, which is preferably sufficient to raise the tubing guide 106 into place before operation of the coiled tubing injector 200. In this example, when the load on the tubing guide 106 exceeds 50% of the rated load of the tubing guide, the pressure in the cylinder 114 would begin increasing beyond the 1,500 psi pressure, and the pressure sensor 302 would begin indicating the compressive load on the strut 110 and/or the load on the tubing guide 106. More generally, the pressure level supplied by the constant-pressure supply 104 may be selected between 50% and 80% of the reference pressure level.
[0057] The cylinder 114 and pressure sensor 302 may be designed for a maximum pressure rating.
The maximum pressure rating may typically be larger than the reference pressure level, for example, 5,000 psi. Thus, the cylinder 114 and pressure sensor 302 may have additional safe sensing range beyond the maximum allowed load (i.e., 3,000 psi pressure in the cylinder 114 and 100% of the load rating of the tubing guide 106) to continue sensing in an overload condition. The maximum pressure rating also ensures that structural failure of the tubing guide 106 occurs before failure of the cylinder 114.
[0058] Turning now to Figure 4, another example of a load-measuring actuator is illustrated.
Similar to the examples shown in Figure 1 and 2, the load-measuring actuator of Figure 4 includes a hydraulic cylinder 12. The hydraulic cylinder 12 has a variable chamber 10.
The variable chamber 10 is delimited by a piston 18 reciprocally disposed in the hydraulic cylinder 12. The variable chamber 10 may be located on the cap side of the hydraulic cylinder 12.
[0059] However, the load-measuring actuator of Figure 4 comprises a course-limiting feature, further described below, configured to leak hydraulic fluid from the variable chamber 10 and avoid the piston 18 traveling full stroke to its end-of-stroke position. In particular, the thermal expansion of the hydraulic fluid in the chamber 10 may not cause the piston 18 to reach the end-of-stroke position. The course-limiting feature is further configured to stop leaking hydraulic fluid from the variable chamber 10 when operating in normal conditions. Therefore, the load-measuring actuator of Figure 4 may not require a constant-pressure supply of hydraulic fluid, and a source 100 of pressurized hydraulic fluid that does not attenuate pressure fluctuations may suffice.
[0060] In the embodiment illustrated in Figure 4, the course-limiting feature comprises a flowpath 84 capable of leaking hydraulic fluid from the variable chamber 10 to a drain 102, and an obturator operatively coupled to the piston 18. As used herein, the obturator normally closes the flowpath 84. The obturator comprises a position sensor 212, a valve 214, and a controller 310. The position sensor 212 may be operatively coupled to the piston 18 to measure a position of the piston 18 relative to the cylinder 12. The valve 214 may be located in the flowpath 84 to control the flow of hydraulic fluid from the variable chamber 10. The valve 214 may be of a type normally-closed, pilot-to-open. The controller 310 may be configured to actuate the valve 214 when the position sensor 212 indicates that the piston 18 is located between a first position, which is recessed from an end-of-stroke position of the piston by a relatively small distance compared to the full stroke (e.g., 10% or less), and the end-of-stroke position. Accordingly, when the cylinder 12 is being extended but has not reached the first position, as well as during operation in noiiiial conditions, the controller 310 may be configured to keep the flowpath 84 closed with valve 214. The controller 310 may further be configured to open the flowpath 84 when the piston 18 is located between the first position and the end-of-stroke position of the piston 18.
[0061] In operation, hydraulic fluid may be supplied from the source 100 to the variable chamber of the hydraulic cylinder 12 to move the piston 18 toward an end-of-stroke position of the piston 18 while the valve 214 closes the flowpath 84. The position of the piston 18 may be continuously measured by the sensor 212, and communicated to the controller 310 for processing.
The controller 310 may selectively open the flowpath 84 based on a comparison between the measured position of the piston 18 and the first position by actuating the valve 214 to its open position. When the valve 214 is open, the hydraulic fluid may leak from the variable chamber 10 into the drain 102. The hydraulic fluid may leak from the variable chamber 10 as long as the piston 18 is located between the first position and the end-of-stroke position. When hydraulic fluid has sufficiently leaked, and the piston position leaves the interval between the first position and the end-of-stroke position, the flowpath 84 may be closed by releasing the valve 214 to its normally-closed position.
[0062] hi cases where environmental temperature increases or heating (e.g., from sunshine) causes thermal expansion of the hydraulic fluid in the variable chamber 10, the thermal expansion is compensated by movement of the piston 18 toward its end-of-stroke position, and possibly by leakage of hydraulic fluid, without spurious increase in pressure of the hydraulic fluid in the variable chamber 10. As such, the pressure measured in the variable chamber 10 remains related to the load applied to the load-measuring actuator, which therefore behaves like a load cell.
[0063] In the embodiment of Figures 5 and 5A, the flowpath 84 extends through the piston 18.
The obturator comprises a check valve 120 biased to close the flowpath 84. The check valve 120 may be integrated into the piston 18. The obturator also includes a pin 222 formed in the cylinder 12 and sized to press against the check valve 120 when the piston 18 is located between the first position and the end-of-stroke position or the piston. When pressed against the check valve 120, the pin 222 opens the check valve 120 and the flowpath 84 to leak hydraulic fluid from the variable chamber 10.
[0064] In the embodiment of Figure 6, the flowpath 84 is provided through a wall of the cylinder 12 and leads to port 130 that is flush with the wall of the cylinder 12. The obturator comprises a seal earned by the piston 18. The seal seals the port 130 from to hydraulic fluid in the variable chamber 10 when the piston 18 is not located between the first position and the end-of-stroke position. The port 130 is exposed to hydraulic fluid in the variable chamber 10 when the piston 18 is located between the first position and the end-of-stroke position.
[0065] To move the piston 18 toward the end-of-stroke position during operation, the flowpath 84 is initially sealed from to the hydraulic fluid in the variable chamber by the seal provided on the piston 18. To leak the hydraulic fluid from the variable chamber 10 when the piston 18 is located between the first position and the end-of-stroke position, the port 130 becomes exposed to the hydraulic fluid in the variable chamber 10 after the piston passes over the port 130, and the flowpath 84 is connected to the variable chamber 10.
[0066] While the disclosure is susceptible to various modifications and alternative forms, specific embodiments thereof are shown by way of example in the drawings and description. It should be understood, however, that the drawings and detailed description thereto are not intended to limit the disclosure to the particular form disclosed, but on the contrary, the intention is to cover all modifications, equivalents and alternatives falling within the spirit and scope of the disclosure.
Claims (19)
supplying a hydraulic fluid at a constant pressure to a chamber of the hydraulic cylinder through a check valve;
trapping the hydraulic fluid in the chamber behind the check valve;
leaking the hydraulic fluid from the chamber at a leakage rate sufficient to compensate for expansion of the hydraulic fluid caused by variations in temperature of the hydraulic fluid, wherein the hydraulic fluid is continuously leaked from the chamber; and measuring the pressure of the hydraulic fluid in the chamber using a pressure sensor.
intermittently supplying the hydraulic fluid from a source to an accumulator;
preventing flow back from the accumulator toward the source; and connecting the accumulator to the chamber of the hydraulic cylinder to supply the hydraulic fluid at the constant pressure.
measuring the pressure of the hydraulic fluid trapped behind the check valve.
Date Recue/Date Received 2022-09-02
adjusting the flow of hydraulic fluid through the restricted flow orifice.
detecting whether the measured pressure exceeds the constant pressure of the hydraulic fluid supplied to the chamber.
a pressure sensor coupled to the variable chamber by a pressure path;
a restricted flow orifice leaking hydraulic fluid from the variable chamber;
and a constant-pressure supply of a hydraulic fluid connected to the variable chamber through a first check valve, wherein the first check valve allows supplying a hydraulic fluid into the variable chamber through the first check valve and prevents flow of the hydraulic fluid out of the variable chamber through the first check valve when in the closed position, and wherein the restricted flow orifice is directly coupled to one of the variable chamber, the flowline, and the pressure path.
the variable chamber is located on the cap side of the hydraulic cylinder;
the first check valve is a normally-closed, pilot-to-open check valve; and the pressure path directly couples the pressure sensor to one of the variable chamber and the flowline.
Date Recue/Date Received 2022-09-02
a source of pressurized hydraulic fluid; and an accumulator intermittently coupled to the source of pressurized hydraulic fluid through a second check valve.
a pressure sensor coupled to the variable chamber by a pressure path;
a flowpath capable of leaking a hydraulic fluid from the variable chamber; and an obturator operatively coupled to a piston, wherein the obturator is configured to open the flowpath when the piston is located between a first position and an end-of-stroke position, wherein thermal expansion of hydraulic fluid in the chamber does not cause the piston to reach the end-of-stroke position.
Date Recue/Date Received 2022-09-02 a position sensor operatively coupled to the piston to measure a position of the piston;
a valve located in the flowpath to control flow of hydraulic fluid from the variable chamber; and a controller actuating the valve when the position sensor indicates that the piston is located between the first position and the end-of-stroke position.
the flowpath extends through the piston, and the obturator comprises a check valve biased to close the flowpath, and a pin formed in the cylinder and sized to press against the check valve when the piston is located between the first position and the end-of-stoke position.
a seal carried by the piston; and a port located on a wall of the cylinder and leading into the flowpath, wherein the seal seals the port from hydraulic fluid in the variable chamber when the piston is not located between the first position and the end-of-stroke position, and the port is exposed to hydraulic fluid in the variable chamber when the piston is located between the first position and the end-of-stroke position.
Date Recue/Date Received 2022-09-02
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/334,981 | 2016-10-26 | ||
US15/334,981 US10352805B2 (en) | 2016-10-26 | 2016-10-26 | Load-measuring hydraulic cylinder |
PCT/US2017/057799 WO2018080958A2 (en) | 2016-10-26 | 2017-10-23 | Load-measuring hydraulic cylinder |
Publications (2)
Publication Number | Publication Date |
---|---|
CA3037586A1 CA3037586A1 (en) | 2018-05-03 |
CA3037586C true CA3037586C (en) | 2024-04-02 |
Family
ID=61969528
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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CA3037586A Active CA3037586C (en) | 2016-10-26 | 2017-10-23 | Load-measuring hydraulic cylinder |
Country Status (5)
Country | Link |
---|---|
US (1) | US10352805B2 (en) |
EP (1) | EP3532734B1 (en) |
CA (1) | CA3037586C (en) |
SG (1) | SG11201903678RA (en) |
WO (1) | WO2018080958A2 (en) |
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CN112761648B (en) * | 2021-01-12 | 2023-03-21 | 盾构及掘进技术国家重点实验室 | Shield that possesses self-checking and safe redundancy impels hydraulic system |
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US4016764A (en) * | 1976-07-19 | 1977-04-12 | The United States Of America As Represented By The Secretary Of The Navy | Temperature compensated, high resolution pressure transducer based on capacitance change principles |
US4655087A (en) * | 1985-08-19 | 1987-04-07 | Rozniecki Edward J | Temperature-compensated pressure gage |
US4673035B1 (en) | 1986-01-06 | 1999-08-10 | Plains Energy Services Ltd | Method and apparatus for injection of tubing into wells |
JPS63166657A (en) * | 1986-12-27 | 1988-07-09 | Nissan Motor Co Ltd | Hydraulic controller for power steering |
DE3934415A1 (en) * | 1989-10-14 | 1991-04-18 | Wabco Westinghouse Fahrzeug | DEVICE FOR MONITORING THE TIGHTNESS OF A GAS-FILLED CHAMBER |
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US6142406A (en) | 1999-04-27 | 2000-11-07 | Newman; Kenneth E. | Method and system for controlling a coiled tubing arch |
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GB2393253B (en) * | 2002-09-18 | 2005-11-16 | Abb Offshore Systems Ltd | Pressure sensing apparatus |
US7677331B2 (en) | 2006-04-20 | 2010-03-16 | Nabors Canada Ulc | AC coiled tubing rig with automated drilling system and method of using the same |
GB0803231D0 (en) | 2008-02-22 | 2008-04-02 | Qserv Ltd | Apparatus and method |
JP5135169B2 (en) * | 2008-10-31 | 2013-01-30 | 日立建機株式会社 | Hydraulic drive unit for construction machinery |
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WO2011107889A2 (en) | 2010-03-03 | 2011-09-09 | Xtreme Coil Drilling Corp. | Coiled tubing injector assembly |
EP2593763A4 (en) * | 2010-07-12 | 2017-12-20 | Custom Fluidpower Pty Ltd | Pressure detection device |
WO2012082728A2 (en) * | 2010-12-13 | 2012-06-21 | Eaton Corporation | Hydraulic system for energy regeneration in a work machine such as a wheel loader |
DE102011103515A1 (en) * | 2011-06-03 | 2012-12-06 | Robert Bosch Gmbh | Hydraulic drive system for a stage with speed-adjustable hydraulic pump as a control |
JP5449264B2 (en) * | 2011-06-30 | 2014-03-19 | 日立建機株式会社 | Hydraulic circuit for counterweight desorption device |
JP6023211B2 (en) * | 2012-11-07 | 2016-11-09 | 日立建機株式会社 | Hydraulic drive unit for construction machinery |
NO340928B1 (en) | 2013-03-11 | 2017-07-17 | C6 Tech As | Petroleum Well Injector System for an Intervention Cable with a Well Tool Run in or Out of a Well in a Well Operation |
WO2015138735A1 (en) * | 2014-03-12 | 2015-09-17 | Actuant Corporation | Hydraulic ram with a side load sensor |
ES2907453T3 (en) * | 2014-05-20 | 2022-04-25 | Wittur Holding Gmbh | SAFETY DEVICE TO OPERATE AN ELEVATOR |
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WO2018080958A3 (en) | 2019-05-31 |
EP3532734B1 (en) | 2023-09-20 |
SG11201903678RA (en) | 2019-05-30 |
EP3532734A4 (en) | 2021-03-03 |
WO2018080958A2 (en) | 2018-05-03 |
US20180113043A1 (en) | 2018-04-26 |
US10352805B2 (en) | 2019-07-16 |
EP3532734A2 (en) | 2019-09-04 |
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